EP1083395B1 - Kombinierter Wärmetauscher mit Verdampfer, Akkumulator und Saugleitung - Google Patents

Kombinierter Wärmetauscher mit Verdampfer, Akkumulator und Saugleitung Download PDF

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Publication number
EP1083395B1
EP1083395B1 EP00307039A EP00307039A EP1083395B1 EP 1083395 B1 EP1083395 B1 EP 1083395B1 EP 00307039 A EP00307039 A EP 00307039A EP 00307039 A EP00307039 A EP 00307039A EP 1083395 B1 EP1083395 B1 EP 1083395B1
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EP
European Patent Office
Prior art keywords
tube
suction line
heat exchanger
evaporator
line heat
Prior art date
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EP00307039A
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English (en)
French (fr)
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EP1083395A1 (de
Inventor
Mark G. Voss
Jonathan P. Wattelet
Stephen B. Memory
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Modine Manufacturing Co
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Modine Manufacturing Co
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/32—Cooling devices
    • B60H1/3204—Cooling devices using compression
    • B60H1/3227—Cooling devices using compression characterised by the arrangement or the type of heat exchanger, e.g. condenser, evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0461—Combination of different types of heat exchanger, e.g. radiator combined with tube-and-shell heat exchanger; Arrangement of conduits for heat exchange between at least two media and for heat exchange between at least one medium and the large body of fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • F28D1/0478—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag the conduits having a non-circular cross-section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0008—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium
    • F28D7/0025—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes
    • F28D7/0033—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one medium being in heat conductive contact with the conduits for the other medium the conduits for one medium or the conduits for both media being flat tubes or arrays of tubes the conduits for one medium or the conduits for both media being bent
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/008—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for vehicles
    • F28D2021/0085—Evaporators

Definitions

  • refrigerants such as R134a are certainly more environmentally friendly than refrigerants such as R12 which it replaced, they nonetheless are undesirable in that they may contribute to the so-called greenhouse effect.
  • Suction line heat exchangers avoid the difficulty by bringing, relatively hot, condensed refrigerant from the outlet of the system condenser or gas cooler into heat exchange relation with the refrigerant being discharged from the evaporator at a location between the evaporator and the compressor. As a consequence, the refrigerant stream exiting the evaporator will be heated.
  • the suction line heat exchanger is sized so that the stream ultimately passed to the compressor from the suction line heat exchanger is a super-heated vapor at a temperature typically several degrees above the saturation temperature of the refrigerant at the pressure at that point in the system. As a consequence, no refrigerant will be in the liquid phase and the compressor will receive only a gaseous refrigerant.
  • typical system of this sort is shown schematically in Fig. 1.
  • Kritzer in US Patent 3,274,797 issued September 27, 1966 discloses a vapor compression refrigeration system, typically used in refrigeration, bringing a capillary tube interconnecting a condenser and evaporator (presumably serving as an expansion device) into contact with the suction line of the compressor to achieve heat exchange therebetween. Kritzer states that this varies the flow rate of refrigerant to the evaporator in response to the temperature of the refrigerant in the suction line to the compressor. While it thus appears that Kritzer is concerned with the exchange of heat between the outlet stream of the evaporator and the inlet stream from the condenser at the expansion device, it is done for the purpose of achieving flow control and therefore is not a suction line heat exchanger in the conventional sense.
  • An exemplary embodiment of the invention achieves the foregoing object in a combined evaporator and suction line heat exchanger for use in a refrigeration system which includes a first elongated, flattened, multi-port tube having a major dimension, a minor dimension measured transverse to the major dimension and opposed ends.
  • the first tube is formed in a serpentine configuration by bends across the minor dimension with a plurality of generally parallel spaced runs between the ends and defining an evaporator.
  • the first tube at the location where it is bonded to the second tube, is at nominal right angles to the runs and is in substantial abutment with some of the bends in the first two.
  • the first tube at the location where it is in contact with second tube, is at a nominal right angle to the runs and in engagement with the bends.
  • Small kinks or knob-like formations are located in the first tube at the location and aligned with and engage corresponding one of the bends. The kinks space small sections of the first tube from the second tube to avoid short-circuiting of the cooling action produced in the first tube.
  • FIG. 2 A preferred embodiment of an evaporator with an integral suction line heat exchanger will be described in connection with the refrigeration system illustrated in Fig. 2.
  • the heat exchanger of the invention is not limited to use in refrigeration systems but may be employed with efficacy where a compact heat exchanger that utilizes gas as one heat exchange fluid to exchange heat with a second heat exchange fluid which in turn may exchange heat with itself or still a third heat exchange fluid.
  • the invention may be employed with efficacy in refrigeration systems employing conventional refrigerants wherein evaporated refrigerant is truly condensed in a condenser as well as more sophisticated systems as, for example, transcritical CO 2 systems, wherein the compressed refrigerant is not literally condensed, but only cooled in a heat exchanger typically referred to as a gas cooler.
  • gas cooler not only refers to a heat exchanger that cools gas as in transcritical CO 2 systems, but also, to a conventional condenser in systems employing conventional refrigerant.
  • the system includes a compressor 10 which provides hot refrigerant at high pressure at an outlet line 12 to a gas cooler 14.
  • a coolant such as ambient air is forced or drawn through the gas cooler 14 by a fan 16 as is well known.
  • a condensed or highly cooled refrigerant at high pressure will exit the gas cooler 14 on a line 18 from which it is flowed to a heat exchanger 20 which is in heat exchange relation with a conventional evaporator 22, and specifically, in heat exchange relation with the evaporator 22 at its outlet side.
  • a fan 24 is employed to drive or draw air to be cooled through the evaporator 22. Some of such air will flow about the heat exchanger 20 as well.
  • the tube 34, intermediate the ends 38, 42 is bent into a serpentine configuration so as to have a plurality of generally parallel runs 46 connected by bends 48.
  • the runs 46 are spaced from one another and extending between adjacent one of the runs 46 are serpentine fins 50.
  • FIG. 6 An alternative embodiment is illustrated in Fig. 6.
  • the same includes an inlet fixture 100 adapted to be connected to an expansion device such as that shown at 26 in Fig. 2.
  • the inlet fixture 100 is connected to a tube 102 that is formed in two sections.
  • the first section, generally designated 103 includes a multiport tube formed of a plurality of generally straight, parallel runs 104 that are interconnected by bends 106.
  • the end of the first section 103 of the tube 102 is connected to be in fluid communication with a tube 108 which extends to a vertically oriented tubular accumulator structure 110.
  • the accumulator 110 is closed at its ends and generally will be of circular or oval cross section.
  • the conduit 108 is in fluid communication with the interior of the tubular structure 110 at a location just below an outlet conduit 112. Both are connected to the tubular structure 110 near its upper end.
  • the first section of the tube 102 defines an air flow path through the evaporator.
  • the accumulator in this particular embodiment, is located closely adjacent to the first section of the tube 102 so as to be in the air flow path therethrough.
  • liquid refrigerant may be in the accumulator 110, the air flow past it will tend to cause the same to be warmed and evaporate during operation of the same.
  • FIG. 7 An alternative embodiment is illustrated in Fig. 7.
  • the embodiment illustrated in Fig. 7 is similar to the embodiment illustrated in Fig. 6 except that the Fig. 7 embodiment is a multicircuit evaporator and the accumulator is to one side of the evaporator. Because of the similarity, where like components are present, like reference numerals will be used.
  • the first section of the tube 102 is replaced by two, hydraulically parallel, serpentine formed tube sections 130 and 132.
  • Both tube sections 130 and 132 are connected to the inlet fixture 100 as well as to a fixture 134 which serves as an inlet to a tubular accumulator assembly 136 which may be the same or identical to the tubular assembly 110.
  • the accumulator 136 is to one side of the tube sections 130 and 132.
  • the tube section 130 includes parallel runs 136 connected by bends 138 while the tubular section 132 includes straight, parallel runs 140, connected by bends 142.
  • the tube sections 130 and 132 are intertwined in a serpentine fashion and serpentine fins 144 are conventionally employed.
  • concern for short-circuiting of the heat transfer paths in the evaporator section of the combined suction line heat exchanger and evaporator may be present. That is to say, in some instances, it is desirable that the cooling capacity of the refrigerant flowing through the evaporator section of the assemblage not be reduced by reason of rejection of heat from the suction line heat exchanger defined by the tube 70 or the tube 120 to the evaporator.
  • the structure illustrated in Fig. 8 may be employed if desired. It is to be particularly understood that while Fig. 8 will be described in connection with the embodiment illustrated in Fig. 6, the structure of Fig. 8 may be advantageously employed in all embodiments if desired.
  • the second tube section 114 where it contacts each of the bends 106, is provided with a shallow, U-shaped kink 152.
  • the kinks 152 are bonded to respective bonds 106 as by brazing.
  • the kinks 152 result in gaps 154 between the second tube 114 and the tube 120 defining the suction line heat exchanger which provides an impediment to heat transfer from the tube 120 to the tube section 102 where the two are in close proximity by reason of the presence of the tube 114.
  • a combined evaporator and suction line heat exchanger made according to the invention is extremely compact. Indeed, the envelope occupied by the evaporator 22 alone is increased minimally, only by the minor dimension d m of the tube 70 and whatever space is occupied by the inlet and outlet fixtures 76 and 78 to the tube 70. While the invention has been illustrated as being a two circuit design, a single circuit apparatus could be employed if desired. In such a case, it would be desirable to eliminate the tube 36 as a result. this would assure countercurrent flow in the tube 70 and the outlet section 58 of the tube 34 for maximum heat exchange efficiency.
  • Capacity can be increased or decreased as desired without changing the frontal area of the overall heat exchanger simply by varying the number of rows A, B, C in the heat exchanger.

Claims (20)

  1. Ein kombinierter Verdampfer- und Saugleitungswärmetauscher (20, 22) zur Verwendung in Klima- und Kühlanlagen, gekennzeichnet durch:
    ein erstes längliches, abgeflachtes Mehrwegrohr (34) mit einer größeren Dimension (Dm), einer kleineren, quer zur größeren Dimension gemessenen, Dimension (dm) und entgegengesetzten Enden (38, 42), wobei besagtes erstes Rohr in einer schlangenförmigen Konfiguration durch Biegungen (48) quer zu besagter kleineren Dimension mit einer Vielheit im Allgemeinen parallel mit Abstand angeordneter Längen (46) zwischen besagten Enden gebildet wird, die einen Verdampfer definieren;
    eine erste Rohreinlassbefestigung (30) an einem der besagten Enden (38);
    eine erste Rohrauslassbefestigung (32) am anderen der besagten Enden (42);
    Rippen (50) die sich zwischen benachbarten der besagten Längen (46) erstrecken;
    ein zweites längliches, abgeflachtes Mehrwegrohr (70) mit: einer Länge, die ein kleiner Bruchteil jener des besagten ersten Rohrs (34) ist, entgegengesetzten Enden (72, 74), einer größeren Dimension (Dm) und einer quer zu besagter größeren Dimension gemessenen kleineren Dimension (dm), wobei besagtes zweite Rohr (70), entlang einer Seitenwand (90), die im Wesentlichen besagte größere Dimension definiert, an eine entsprechende Seitenwand des besagten ersten Rohrs (34) an einer Stelle unmittelbar stromaufwärts der besagten Auslassbefestigung bondiert ist, um in einem guten Wärmetauschverhältnis damit zu stehen, um einen Saugleitungswärmetauscher zu definieren;
    eine Saugleitungseinlassbefestigung (76) an einem besagter zweiten Rohrenden (70); und
    eine Saugleitungsauslassbefestigung (78) an einem besagter zweiten Rohrenden (70); und
  2. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 1, worin besagtes erste Rohr (34), an besagter Stelle (58), in einem nominellen rechten Winkel zu besagten Längen (46) und in wesentlichem Eingriff mit einigen der besagten Biegungen (48) ist.
  3. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 2, weiter ein drittes, längliches, abgeflachtes Mehrwegrohr (36) einschließend, das einem umgekehrten Abbild besagten ersten Rohrs ähnlich ist, und eine größere Dimension (Dm), eine kleinere, quer zur größeren Dimension gemessene, Dimension (dm) und entgegengesetzte Enden (40, 44) aufweist, wobei besagtes dritte Rohr in einer schlangenförmigen Konfiguration durch Biegungen (48) quer zu seiner kleinen Dimension mit einer Vielheit von im Allgemeinen parallelen, mit Abstand angeordneten Längen (46) zwischen Enden davon gebildet wird, und sich Rippen (50) zwischen benachbarten Drittrohrlängen erstrecken, wobei eins der besagten Drittrohrenden in Fluidkommunikation mit besagter Einlassbefestigung (30) des ersten Rohrs steht, das andere der besagten Drittrohrenden in Fluidkommunikation mit besagter Auslassbefestigung (32) steht, um, zusammen mit besagtem ersten Rohr (34), einen Mehrkreisverdampfer zu definieren, wobei besagtes zweite Rohr (36) weiter zwischen seinen Enden an besagtes dritte Rohr (70) an einer Stelle unmittelbar stromaufwärts der besagten ersten Auslassbefestigung (32) bondiert wird, um damit in einem Wärmetauschverhältnis zu sein.
  4. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 3, worin besagtes dritte Rohr (36) ein Spiegelbild des besagten ersten Rohrs (34) ist.
  5. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 3, worin die Zahl der besagten Längen (46) in besagtem ersten Rohr (34) der Zahl der besagten Längen (46) in besagtem dritten Rohr (36) gleich ist.
  6. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 1, worin sich besagte Saugleitungsaustassbefestigung (78) hydraulisch zwischen besagten Einlass- und Auslassbefestigungen des ersten Rohrs befindet, um für Gegenströmung in besagtem Saugleitungswärmetauscher zu sorgen.
  7. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 1, worin es eine Vielheit besagter ersten Rohre (34) in gestapelter Beziehung von einer Seite des besagten kombinierten Verdampfer- und Saugleitungswärmetauschers zur anderen gibt und entsprechende eine Enden der besagten ersten Rohre an besagte Einlassbefestigung (30) erster Rohre angeschlossen sind und entsprechende andere Enden der besagten ersten Rohre an besagte Auslassbefestigung (32) erster Rohre angeschlossen sind.
  8. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 1, worin besagtes zweite Rohr (70) nominell gerade ist.
  9. Der Kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 1, worin besagte Einlass- und Auslassbefestigungen (30, 32) besagten ersten Rohrs einen einzelnen Befestigungsblock definieren.
  10. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 1, worin besagtes erstes Rohr in zwei separaten Abschnitten ist, ein besagter Abschnitt (103) besagte im Allgemeinen parallele, mit Abstand angeordnete Längen einschließt und sich der andere besagte Abschnitt (114) an besagter Stelle befindet; und ein Speicher (110) besagte Abschnitte verbindet.
  11. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs10, worin besagter Speicher (110) eine vertikal verlängerte röhrenförmige Struktur ist.
  12. Der kombinierte Verdampfer- und Saugleitungswärmespeicher des Anspruchs 11, worin besagter andere Abschnitt (114) an besagte rohrförmige Struktur (110) oberhalb eines Anschlusspunktes des besagten einen Abschnitts (103) an besagte rohrförmige Struktur angeschlossen ist.
  13. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs10, worin besagter Speicher (136) auf einer Seite der besagten zwei Abschnitte positioniert ist.
  14. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 10, worin besagter eine Abschnitt (103) einen Luftstrompfad durch den Verdampfer definiert und sich besagter Speicher (110) neben besagtem einen Abschnitt in besagtem Luftstrompfad befindet.
  15. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 10, worin es zwei besagter Einrohrabschnitte (130,132) gibt, die miteinander verschlungen sind, um einen Mehrkreisverdampfer zu definieren.
  16. Der kombinierte Verdampfer- und Saugleitungswärmetauscher des Anspruchs 1, worin besagtes erstes Rohr (103), an besagter Stelle, in einem nominell rechten Winkel zu besagten Lägen (104) und in Eingriff mit besagten Biegungen (102) ist; und Abknickungen (152) in besagtem ersten Rohr an besagter Stelle, die mit entsprechenden der besagten Biegungen fluchten und in Eingriff stehen, wobei besagte Abknickungen mit Abstand von besagtem zweiten Rohr (120) angeordnet sind.
  17. Ein Zweikreisverdampfer mit einem integralen Saugleitungswärmetauscher, gekennzeichnet durch:
    ein Paar länglicher, abgeflachter Mehrwegrohre (34, 36), jedes mit entgegengesetzten Enden und zu einer schlangenförmigen Konfiguration geformt, um Abschnitte mit einer Vielheit, mit Abstand angeordneter, parallelen Längen (46) zu definieren, wobei das eine der besagten Enden jedes Rohrs hydraulisch nahe dem entsprechenden Einlauflauf ist, der ein Einlassende (38, 40) ist und das andere der Enden jedes Rohrs ein Auslassende (42, 44) ist, sich ein Abschnitt (58) jedes Rohrs eben stromaufwärts des besagten Auslassendes entlang einer Seite des entsprechenden Abschnitts in einer Richtung allgemein quer zu den Längen (46) davon zu einer Position auf einer anderen Seite des entsprechenden Abschnitts neben besagtem Einlasslauf erstreckt;
    besagte Abschnitte in Bezug zu einander so orientiert sind, dass besagte Einlasslängen nebeneinander liegen und besagte stromaufwärts Abschnitte (58) miteinander fluchten;
    eine Einlassbefestigung (30), die an beide besagten Einlassenden angeschlossen ist;
    eine Auslassbefestigung (32), die an beide besagten Auslassenden angeschlossen ist; und
    ein zusätzliches, längliches, abgeflachtes Mehrwegrohr (70), da sich entlang besagter stromaufwärts Abschnitte (58) in Wärmetauscherbeziehung damit erstreckt, um einen Saugleitungswärmetauscher zu definieren.
  18. Der Zweikreisverdampfer mit einem integralen Saugleitungswärmetauscher des Anspruchs 17, worin besagtes zusätzliche Rohr (70) ein nominell gerades, an besagte stromaufwärts Abschnitte (58) bondiertes, Rohr ist und entgegengesetzte Enden (72, 74), zwischen denen sich besagte Abschnitte befinden, einen Einlassanschluss (76) an einem der zusätzlichen Rohrenden, und einen Auslassanschluss (78) am anderen der besagten zusätzlichen Rohrenden aufweist.
  19. Der Zweikreisverdampfer mit einem integralen Saugteitungswärmetauscher des Anspruchs 17, der weiter Rippen (50) einschließt, die sich zwischen benachbarten der besagten Längen erstrecken.
  20. Der Zweikreisverdampfer mit einem integralen Saugleitungswärmetauscher des Anspruchs 17, worin die Rohre (34, 36) des besagten Paars miteinander identisch sind und so orientiert sind, dass eins als das Spiegelbild des anderen erscheint.
EP00307039A 1999-09-07 2000-08-17 Kombinierter Wärmetauscher mit Verdampfer, Akkumulator und Saugleitung Expired - Lifetime EP1083395B1 (de)

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US390818 1999-09-07
US09/390,818 US6185957B1 (en) 1999-09-07 1999-09-07 Combined evaporator/accumulator/suctionline heat exchanger

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JP2001091104A (ja) 2001-04-06
BR0003878A (pt) 2001-04-03
DE60011196D1 (de) 2004-07-08
AU768858B2 (en) 2004-01-08
CN1171053C (zh) 2004-10-13
US6185957B1 (en) 2001-02-13
DE60011196T2 (de) 2005-06-23
TW448278B (en) 2001-08-01
MXPA00008667A (es) 2002-04-24
CA2317372A1 (en) 2001-03-07
RU2271503C2 (ru) 2006-03-10
AR025501A1 (es) 2002-11-27
KR20010030262A (ko) 2001-04-16
EP1083395A1 (de) 2001-03-14
CN1292485A (zh) 2001-04-25
ES2220348T3 (es) 2004-12-16
MY133661A (en) 2007-11-30
ATE268458T1 (de) 2004-06-15

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